JP2014156822A - Bearing device for turbocharger - Google Patents

Bearing device for turbocharger Download PDF

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JP2014156822A
JP2014156822A JP2013028137A JP2013028137A JP2014156822A JP 2014156822 A JP2014156822 A JP 2014156822A JP 2013028137 A JP2013028137 A JP 2013028137A JP 2013028137 A JP2013028137 A JP 2013028137A JP 2014156822 A JP2014156822 A JP 2014156822A
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Prior art keywords
outer ring
engine oil
spacer
ring spacer
housing
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JP6048195B2 (en
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Chiaki Saito
千晃 齋藤
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JTEKT Corp
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JTEKT Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
    • F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
    • F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/23—Gas turbine engines
    • F16C2360/24—Turbochargers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supercharger (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To prevent increase of a bearing torque caused by that engine oil resides in an annular gap to increase an agitation resistance of the engine oil in a rolling bearing.SOLUTION: A bearing device for a turbocharger includes, in an inner peripheral side of an outer ring housing 10, a cylindrical outer ring spacer 13 both end faces 35 in the axial direction of which come into contact with end faces 27 of outer rings 22 to maintain a gap between rolling bearings 20. An inner diameter 13R of the outer ring spacer 13 is larger than an inner diameter 22R of the outer ring 22, and a center shaft 13A of the outer ring spacer 13 is eccentric downward with respect to a center shaft 22A of the outer ring 22.

Description

本発明は、ターボチャージャに用いられる軸受装置に関する。   The present invention relates to a bearing device used for a turbocharger.

高速回転する回転軸をケーシング内で支持するターボチャージャ用の軸受装置として、図４に示すように、ケーシング９０内に設けられている円筒形状の外輪ハウジング９１と、この外輪ハウジング９１の軸方向両側部それぞれに取り付けられている転がり軸受９２とを備え、これら転がり軸受９２が、外輪ハウジング９１の径方向内側にある回転軸９９を回転自在に支持するものがある（特許文献１参照）。   As shown in FIG. 4, a cylindrical outer ring housing 91 provided in the casing 90 and both axial sides of the outer ring housing 91 as a bearing device for a turbocharger that supports a rotating shaft that rotates at a high speed in the casing. There are rolling bearings 92 attached to the respective parts, and these rolling bearings 92 rotatably support a rotating shaft 99 on the radially inner side of the outer ring housing 91 (see Patent Document 1).

図４に示すターボチャージャでは、ケーシング９０に給油孔９６が設けられており、この給油孔９６から外輪ハウジング９１の外周面９１ａへとエンジンオイルの一部が供給される。このエンジンオイルにより、ケーシング９０の内周面９０ａと外輪ハウジング９１の外周面９１ａとの間に油膜（オイルフィルム）が形成され、軸受装置９７の振動がケーシング９０に伝わりにくくすることが可能となる。   In the turbocharger shown in FIG. 4, an oil supply hole 96 is provided in the casing 90, and a part of the engine oil is supplied from the oil supply hole 96 to the outer peripheral surface 91 a of the outer ring housing 91. With this engine oil, an oil film (oil film) is formed between the inner peripheral surface 90 a of the casing 90 and the outer peripheral surface 91 a of the outer ring housing 91, and the vibration of the bearing device 97 can be made difficult to be transmitted to the casing 90. .

また、ケーシング９０の内周面９０ａと外輪ハウジング９１の外周面９１ａとの間に供給されたエンジンオイルは、図４の矢印で示すように、外輪ハウジング９１の軸方向の端面９８とケーシング９０内の側壁面９０ｂとの間を経て転がり軸受９２内に供給され、このエンジンオイルにより転がり軸受９２を潤滑すると共に冷却することが可能となる。   Further, the engine oil supplied between the inner peripheral surface 90a of the casing 90 and the outer peripheral surface 91a of the outer ring housing 91, as indicated by the arrows in FIG. It is supplied into the rolling bearing 92 through the space between the side wall surface 90b of the roller and the rolling bearing 92 can be lubricated and cooled by the engine oil.

回転軸９９の外周側には、転がり軸受９２の内輪９２ａの相互の間隔を保持するための内輪間座９９ａが取り付けられており、外輪ハウジング９１の内周側には、外輪９２ｂの相互の間隔を保持するための外輪間座９１ｂが設けられている。そして、内輪間座９９ａと外輪間座９１ｂの間には環状空間１００が形成されている。ターボチャージャに使用される軸受装置は、径方向の寸法的な制約が大きく、例えば、外輪ハウジング９１の直径は２０ｍｍ程度であり、環状空間１００の径方向の最小寸法は、１〜１．５ｍｍ程度と非常に狭いものとなっている。また、外輪ハウジング９１の軸方向の中央下部にはエンジンオイルの排出孔８９が形成されている。なお、内輪９２ａの環状空間１００側端部の内径と内輪間座９９ａの内径とは、ほぼ等しくなっており、外輪９２ｂの環状空間１００側端部の内径と外輪間座９１ｂの内径とは、ほぼ等しくなっている。   An inner ring spacer 99a is attached to the outer peripheral side of the rotating shaft 99 to maintain the mutual spacing of the inner rings 92a of the rolling bearing 92, and the outer spacing 92b is spaced from the inner peripheral side of the outer ring housing 91. An outer ring spacer 91b is provided. An annular space 100 is formed between the inner ring spacer 99a and the outer ring spacer 91b. The bearing device used in the turbocharger has large dimensional restrictions in the radial direction. For example, the diameter of the outer ring housing 91 is about 20 mm, and the minimum dimension in the radial direction of the annular space 100 is about 1 to 1.5 mm. It is very narrow. Further, an engine oil discharge hole 89 is formed in the axially lower center portion of the outer ring housing 91. Note that the inner diameter of the inner ring 92a end portion on the annular space 100 side is substantially equal to the inner diameter of the inner ring spacer 99a, and the inner diameter of the outer ring 92b end portion on the annular space 100 side and the inner diameter of the outer ring spacer 91b are It is almost equal.

特開２０１０−１３３２６６号公報JP 2010-133266 A

前記のとおり、ターボチャージャのケーシング９０側から供給されたエンジンオイルは、転がり軸受９２を潤滑すると共に冷却するためにも機能するが、この潤滑及び冷却に要する量を超えるエンジンオイルが、転がり軸受９２内に供給された場合、この転がり軸受９２を通過したエンジンオイルが、上述の如く、幅の狭い環状空間１００で滞留し、高速で回転する転がり軸受９２内におけるエンジンオイルの撹拌抵抗が大きくなる。この結果、軸受トルクが増大し、ターボチャージャとしての機能を十分に発揮させることができなくなるおそれがある。   As described above, the engine oil supplied from the casing 90 side of the turbocharger functions to lubricate and cool the rolling bearing 92. However, the engine oil exceeding the amount required for this lubrication and cooling is reduced to the rolling bearing 92. When supplied to the inside, the engine oil that has passed through the rolling bearing 92 stays in the narrow annular space 100 as described above, and the stirring resistance of the engine oil in the rolling bearing 92 that rotates at a high speed increases. As a result, the bearing torque increases, and the function as a turbocharger may not be fully exhibited.

なお、軸方向両側の転がり軸受９２間に形成されている環状空間１００の過剰なエンジンオイルを、排出孔８９を通じて軸受装置９７外へ排出可能であるが、エンジンオイルの供給量に比べて排出量が十分でない場合、環状空間１００でエンジンオイルが滞留してしまい、転がり軸受９２内におけるエンジンオイルの撹拌抵抗が大きくなる。   Excess engine oil in the annular space 100 formed between the rolling bearings 92 on both axial sides can be discharged out of the bearing device 97 through the discharge hole 89, but the discharge amount is larger than the supply amount of the engine oil. Is not sufficient, the engine oil stays in the annular space 100, and the agitation resistance of the engine oil in the rolling bearing 92 increases.

そこで、本発明は、環状空間にエンジンオイルが滞留して転がり軸受におけるエンジンオイルの撹拌抵抗が大きくなることに起因して軸受トルクが増大するのを抑制できる軸受装置を提供することを目的とする。   SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a bearing device that can suppress an increase in bearing torque caused by engine oil remaining in an annular space and increasing agitation resistance of engine oil in a rolling bearing. .

上記目的を達成する本発明は、ケーシング内に設けられ水平な軸方向の中央下部にエンジンオイルの排出孔が形成されている円筒形状の外輪ハウジングと、前記外輪ハウジングの軸方向両側部それぞれに取り付けられ、外輪、内輪及び転動体を備え前記外輪ハウジングの径方向内側にある回転軸を回転自在に支持する転がり軸受と、前記内輪の相互間に介在し、前記内輪の相互間の間隔を保持する円筒状の内輪間座と、前記外輪の相互間に介在し、前記外輪の相互間の間隔を保持する円筒状の外輪間座と、を有し、前記ケーシングの内周面と前記外輪ハウジングの外周面との間に供給されたエンジンオイルが、前記外輪ハウジングの軸方向の端面と前記ケーシング内の側壁面との間を経て前記転がり軸受内に供給され、前記転がり軸受を通過したエンジンオイルが、前記内輪間座と外輪間座との間の環状空間から前記排出孔を通じて排出されるターボチャージャ軸受装置であって、前記外輪間座の内径が前記外輪の内径に比べて大きく、かつ、前記外輪間座の中心軸が前記外輪の中心軸に対して下方に偏心していることを特徴とする。   The present invention that achieves the above-described object includes a cylindrical outer ring housing that is provided in a casing and has an engine oil discharge hole formed in a horizontal lower central portion in the axial direction, and is attached to both axial sides of the outer ring housing. A rolling bearing that includes an outer ring, an inner ring, and a rolling element and rotatably supports a rotating shaft that is radially inward of the outer ring housing; and an inner ring that is interposed between the inner rings and maintains a distance between the inner rings. A cylindrical inner ring spacer, and a cylindrical outer ring spacer interposed between the outer rings and maintaining a space between the outer rings, the inner peripheral surface of the casing and the outer ring housing The engine oil supplied between the outer peripheral surface and the outer ring housing passes between the axial end surface of the outer ring housing and the side wall surface of the casing and is supplied into the rolling bearing and passes through the rolling bearing. The engine oil is discharged from the annular space between the inner ring spacer and the outer ring spacer through the discharge hole, and the inner diameter of the outer ring spacer is larger than the inner diameter of the outer ring. The center axis of the outer ring spacer is eccentric downward with respect to the center axis of the outer ring.

本発明のターボチャージャ用軸受装置は、外輪間座の内径が外輪の内径に比べて大きく、かつ、外輪間座の中心軸が外輪の中心軸に対して下方に偏心している構成である。このため、外輪間座の内径と外輪の内径がほぼ等しく、これらの中心軸が一致している従来の軸受装置に比べて、外輪ハウジングと内輪間座との間に形成されている環状空間の径方向の最小寸法を、外輪ハウジング及び回転軸の下方部分において広くとることができる。これにより、外輪ハウジングに設けられている排出孔からエンジンオイルを充分に排出することができ、前記環状空間にエンジンオイルが滞留することに起因して転がり軸受内のエンジンオイルの撹拌抵抗が大きくなるのを抑制することができる。したがって、軸受トルクが増大するのを抑制することができる。   The turbocharger bearing device of the present invention has a configuration in which the inner diameter of the outer ring spacer is larger than the inner diameter of the outer ring, and the central axis of the outer ring spacer is eccentric downward with respect to the central axis of the outer ring. For this reason, compared with the conventional bearing device in which the inner diameter of the outer ring spacer is substantially equal to the inner diameter of the outer ring and the central axes thereof coincide, the annular space formed between the outer ring housing and the inner ring spacer is smaller. The smallest radial dimension can be widened in the outer ring housing and the lower part of the rotating shaft. As a result, the engine oil can be sufficiently discharged from the discharge hole provided in the outer ring housing, and the agitation resistance of the engine oil in the rolling bearing increases due to the engine oil remaining in the annular space. Can be suppressed. Therefore, an increase in bearing torque can be suppressed.

また、前記ターボチャージャ用軸受装置は、前記外輪ハウジングの内周面に、前記排出孔に向かうにしたがって下方へ傾斜するテーパ面を設けていることが好ましい。この場合、テーパ面に沿ってエンジンオイルが排出孔に流れ込みやすくなり、エンジンオイル排出性が向上する。その結果、転がり軸受内のエンジンオイルの撹拌抵抗が大きくなるのをより効果的に抑制することができ、軸受トルクが増大するのをより効果的に抑制することができる。   In the turbocharger bearing device, it is preferable that a tapered surface inclined downward toward the discharge hole is provided on the inner peripheral surface of the outer ring housing. In this case, engine oil can easily flow into the discharge hole along the tapered surface, and engine oil discharge performance is improved. As a result, it is possible to more effectively suppress an increase in the stirring resistance of engine oil in the rolling bearing, and it is possible to more effectively suppress an increase in bearing torque.

本発明の軸受装置によれば、環状空間にエンジンオイルが滞留することに起因して転がり軸受内におけるエンジンオイルの撹拌抵抗が大きくなるのを抑制することができるので、軸受トルクが増大するのを抑制することができる。   According to the bearing device of the present invention, it is possible to suppress an increase in the agitation resistance of the engine oil in the rolling bearing due to the engine oil remaining in the annular space. Can be suppressed.

本発明の軸受装置が組み込まれているターボチャージャの拡大縦断面図である。1 is an enlarged longitudinal sectional view of a turbocharger incorporating a bearing device of the present invention. 軸受装置の拡大縦断面図である。It is an enlarged vertical sectional view of a bearing device. 外輪間座と外輪の内径及び中心軸の関係を示す説明図である。It is explanatory drawing which shows the relationship between the inner ring | wheel inner diameter of a outer ring spacer, an outer ring | wheel, and a central axis. 従来の軸受装置の拡大縦断面図である。It is an enlarged vertical sectional view of a conventional bearing device.

以下、本発明の実施の形態を図面に基づいて説明する。
図１は本発明のターボチャージャ用軸受装置１（以下、単に軸受装置１という）が組み込まれているターボチャージャＴの縦断面図である。このターボチャージャＴは、自動車用のものであって、ケーシング２と、このケーシング２内で高速回転する回転軸３とを備えている。回転軸３は、中心軸Ｌを水平方向に向けた状態で配置されており、その軸方向の一方側（図１の右側）の端部にはタービン５３が、他方側（図１の左側）の端部にはインペラ５４がそれぞれ取り付けられている。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a turbocharger T in which a turbocharger bearing device 1 of the present invention (hereinafter simply referred to as a bearing device 1) is incorporated. The turbocharger T is for an automobile and includes a casing 2 and a rotating shaft 3 that rotates at high speed in the casing 2. The rotating shaft 3 is arranged with the central axis L oriented in the horizontal direction, and the turbine 53 is located at the end of one axial side (the right side in FIG. 1) and the other side (the left side in FIG. 1). Impellers 54 are respectively attached to the end portions.

ケーシング２の軸方向一方側には排気流路５１が設けられており、軸方向他方側には給気流路５５が設けられている。排気流路５１を流れる排気ガスによりタービン５３が回転することで回転軸３は高速回転し、この回転軸３の回転力によってインペラ５４は給気流路５５内で回転する。そして、給気流路５５の開口部から吸引された空気がインペラ５４により圧縮され、この圧縮された空気が、ガソリンや軽エンジンオイル等の燃料と共に、図示しないエンジンのシリンダ室内に送り込まれる。   An exhaust passage 51 is provided on one side of the casing 2 in the axial direction, and an air supply passage 55 is provided on the other side in the axial direction. When the turbine 53 is rotated by the exhaust gas flowing through the exhaust passage 51, the rotating shaft 3 rotates at a high speed, and the impeller 54 rotates in the air supply passage 55 by the rotational force of the rotating shaft 3. The air sucked from the opening of the air supply passage 55 is compressed by the impeller 54, and the compressed air is sent into a cylinder chamber of an engine (not shown) together with fuel such as gasoline and light engine oil.

このようなターボチャージャＴの回転軸３は、数万〜十数万（回／分）もの高速で回転し、しかも、エンジンの運転状況（回転数）に応じて回転速度が頻繁に変化することから、回転軸３の回転損失をできるだけ低減するのが好ましい。そこで、ケーシング２内に設けられている軸受装置１で回転軸３を支持することにより、回転軸３の回転抵抗を小さくしている。   The rotating shaft 3 of such a turbocharger T rotates at a high speed of several tens of thousands to several tens of thousands (times / minute), and the rotation speed frequently changes according to the operating state (the number of rotations) of the engine. Therefore, it is preferable to reduce the rotation loss of the rotating shaft 3 as much as possible. Therefore, the rotational resistance of the rotary shaft 3 is reduced by supporting the rotary shaft 3 with the bearing device 1 provided in the casing 2.

図２は軸受装置１の縦断面図である。この軸受装置１は、ケーシング２内に設けられ円筒形状である外輪ハウジング１０と、この外輪ハウジング１０の軸方向両側に取り付けられた一対の転がり軸受２０とを備えている。これら転がり軸受２０により、外輪ハウジング１０の内部を挿通している回転軸３が回転自在に支持される。   FIG. 2 is a longitudinal sectional view of the bearing device 1. The bearing device 1 includes a cylindrical outer ring housing 10 provided in the casing 2 and a pair of rolling bearings 20 attached to both sides in the axial direction of the outer ring housing 10. By these rolling bearings 20, the rotating shaft 3 inserted through the outer ring housing 10 is rotatably supported.

軸受装置１は、ケーシング２の中央部に設けられた収容室４に収容されている。この収容室４は、ケーシング２の内周面５と、この内周面５の軸方向両側からそれぞれ径方向内側に延びる円環状の側壁面６とによって区画される領域である。収容室４の内周面５は、回転軸３と同芯の円周面に形成されている。   The bearing device 1 is accommodated in an accommodation chamber 4 provided at the center of the casing 2. The storage chamber 4 is a region defined by an inner peripheral surface 5 of the casing 2 and an annular side wall surface 6 extending radially inward from both axial sides of the inner peripheral surface 5. The inner peripheral surface 5 of the storage chamber 4 is formed on a circumferential surface concentric with the rotation shaft 3.

また、ケーシング２には、収容室４の内周面５において開口する給油孔７及び排油孔８が形成されている。給油孔７は、ケーシング２の上部の二箇所に形成されており、この給油孔７を通じて、エンジンオイルが外輪ハウジング１０の外周面１６とケーシング２の内周面５との間に供給される。排油孔８は、ケーシング２の下部の軸方向中央部に形成されており、収容室４内に設けられている軸受装置１を通過したエンジンオイルを、この排油孔８を通じて外部へと排出する。   Further, the casing 2 is formed with an oil supply hole 7 and an oil discharge hole 8 that are opened in the inner peripheral surface 5 of the storage chamber 4. The oil supply holes 7 are formed at two locations on the upper portion of the casing 2, and engine oil is supplied between the outer peripheral surface 16 of the outer ring housing 10 and the inner peripheral surface 5 of the casing 2 through the oil supply holes 7. The oil drain hole 8 is formed in the axial center of the lower portion of the casing 2, and the engine oil that has passed through the bearing device 1 provided in the storage chamber 4 is discharged to the outside through the oil drain hole 8. To do.

外輪ハウジング１０は、軸方向両側の軸受保持部１１及びその間の本体部１９を含み、これらが一体として構成されている円筒形状の部材である。そして、外輪ハウジング１０の軸方向の中央下部に、エンジンオイルの排出孔１５が形成されている。排出孔１５は、ケーシング２の排油孔８と連続する配置となる。
なお、外輪ハウジング１０は、ケーシング２内において、図示しない止定手段によって周方向の回転が制限されている。 The outer ring housing 10 is a cylindrical member that includes bearing holding portions 11 on both sides in the axial direction and a main body portion 19 therebetween, and these are integrally formed. An engine oil discharge hole 15 is formed in a lower central portion of the outer ring housing 10 in the axial direction. The discharge hole 15 is arranged continuously with the oil discharge hole 8 of the casing 2.
The outer ring housing 10 is restricted from rotating in the circumferential direction in the casing 2 by a fixing means (not shown).

また、外輪ハウジング１０の軸方向両側の端面１７は、収容室４を区画する前記側壁面６に、隙間を有して対向している。なお、外輪ハウジング１０の軸方向の端面１７と、ケーシング２の側壁面６との間には微小の隙間が形成されるが、図２では、説明を容易とするためにこの隙間を大きくして表現している。   Further, the end faces 17 on both sides in the axial direction of the outer ring housing 10 are opposed to the side wall face 6 defining the storage chamber 4 with a gap. A minute gap is formed between the end surface 17 in the axial direction of the outer ring housing 10 and the side wall surface 6 of the casing 2. In FIG. expressing.

本実施形態において各転がり軸受２０はアンギュラ玉軸受である。転がり軸受２０それぞれは、外輪２２、内輪２３、転動体としての複数の玉２４、及び各玉２４を一定間隔毎に保持する保持器２８を有している。玉２４はセラミック製である。
外輪２２は、外輪ハウジング１０の軸方向両側に設けられた短筒状の軸受保持部１１の内周面３１に内嵌しており、内輪２３は回転軸３に外嵌している。 In this embodiment, each rolling bearing 20 is an angular ball bearing. Each of the rolling bearings 20 includes an outer ring 22, an inner ring 23, a plurality of balls 24 as rolling elements, and a cage 28 that holds the balls 24 at regular intervals. The ball 24 is made of ceramic.
The outer ring 22 is fitted on the inner peripheral surface 31 of the short cylindrical bearing holding portion 11 provided on both axial sides of the outer ring housing 10, and the inner ring 23 is fitted on the rotary shaft 3.

外輪ハウジング１０の本体部１９の内周側には、円筒形状の外輪間座１３が一体形成されている。図２においては、左右の軸受保持部１１の内周面３１どうしを結ぶ仮想面Ｃよりも径方向内側に位置する部分が、外輪間座１３として構成されている。この外輪間座１３の軸方向の両端部３３は、中央部に対して縮径されており、その軸方向外側の両端面３５が外輪２２の軸方向内側の端面２７に当接している。この外輪間座１３により左右の外輪２２の相互の間隔が保持されている。   A cylindrical outer ring spacer 13 is integrally formed on the inner peripheral side of the main body 19 of the outer ring housing 10. In FIG. 2, a portion located radially inward from a virtual surface C connecting the inner peripheral surfaces 31 of the left and right bearing holding portions 11 is configured as an outer ring spacer 13. Both end portions 33 in the axial direction of the outer ring spacer 13 are reduced in diameter with respect to the central portion, and both end surfaces 35 on the outer side in the axial direction are in contact with end surfaces 27 on the inner side in the axial direction of the outer ring 22. The outer ring spacer 13 holds the distance between the left and right outer rings 22.

また、一対の内輪２３の相互間には、円筒体からなる内輪間座９を介在しており、この内輪間座９内を回転軸３が挿通している。内輪間座９の両端面は内輪２３の軸方向内側の端面に当接しており、この内輪間座９により左右の内輪２３の相互間の間隔が保持されている。
この様にして、外輪間座１３及び内輪間座９により、転がり軸受２０相互間の間隔が保持される。また、外輪ハウジング１０と内輪間座９との間には、環状空間５０が形成されている。 Further, an inner ring spacer 9 made of a cylindrical body is interposed between the pair of inner rings 23, and the rotary shaft 3 is inserted through the inner ring spacer 9. Both end surfaces of the inner ring spacer 9 are in contact with an end surface on the inner side in the axial direction of the inner ring 23, and the inner ring spacer 9 maintains a distance between the left and right inner rings 23.
Thus, the space between the rolling bearings 20 is maintained by the outer ring spacer 13 and the inner ring spacer 9. An annular space 50 is formed between the outer ring housing 10 and the inner ring spacer 9.

そして、本実施形態では、前記給油孔７から供給されたエンジンオイルにより、ケーシング２の内周面５と外輪ハウジング１０の外周面１６との間に油膜（オイルフィルム）が形成され、軸受装置１の振動がケーシング２に伝わりにくくなっている。
これら内周面５と外周面１６との間に供給されたエンジンオイルは、軸方向両側それぞれにおいて、外輪ハウジング１０の軸方向の端面１７とケーシング２内の側壁面６との間を経て、転がり軸受２０内に供給される。つまり、エンジンオイルは、外輪２２と内輪２３との間の環状の軸受空間Ｑに供給される。そして、転がり軸受２０それぞれを通過したエンジンオイル（軸受空間Ｑを通過したエンジンオイル）は、前記環状空間５０を流れ、さらに、この環状空間５０から排出孔１５及び排油孔８を通じて外部へ排出される。 In the present embodiment, an oil film (oil film) is formed between the inner peripheral surface 5 of the casing 2 and the outer peripheral surface 16 of the outer ring housing 10 by the engine oil supplied from the oil supply hole 7. Is difficult to be transmitted to the casing 2.
The engine oil supplied between the inner peripheral surface 5 and the outer peripheral surface 16 rolls between the axial end surface 17 of the outer ring housing 10 and the side wall surface 6 in the casing 2 on both sides in the axial direction. It is supplied into the bearing 20. That is, the engine oil is supplied to the annular bearing space Q between the outer ring 22 and the inner ring 23. The engine oil that has passed through each of the rolling bearings 20 (engine oil that has passed through the bearing space Q) flows through the annular space 50, and is further discharged from the annular space 50 to the outside through the discharge holes 15 and the oil discharge holes 8. The

図３は、外輪間座１３の両端部３３の内径１３Ｒと外輪２２の内周面２６の内径２２Ｒとの関係、及び外輪間座１３の中心軸１３Ａと外輪２２の中心軸２２Ａとの位置関係を示す説明図である。図３に示すように、外輪間座１３の内径１３Ｒは、外輪２２の内径２２Ｒよりも大きくなるように設定されている。また、外輪間座１３の中心軸１３Ａは、外輪２２の中心軸２２Ａ、つまり回転軸３の中心軸Ｌに対して下方に偏心している。この偏心量Ｘは、外輪間座１３の前記内径１３Ｒと外輪２２の前記内径２２Ｒとの差のほぼ半分に設定されている。   FIG. 3 shows the relationship between the inner diameter 13R of both end portions 33 of the outer ring spacer 13 and the inner diameter 22R of the inner peripheral surface 26 of the outer ring 22, and the positional relationship between the central axis 13A of the outer ring spacer 13 and the central axis 22A of the outer ring 22. It is explanatory drawing which shows. As shown in FIG. 3, the inner diameter 13 </ b> R of the outer ring spacer 13 is set to be larger than the inner diameter 22 </ b> R of the outer ring 22. Further, the center axis 13 </ b> A of the outer ring spacer 13 is eccentric downward with respect to the center axis 22 </ b> A of the outer ring 22, that is, the center axis L of the rotating shaft 3. The eccentric amount X is set to be approximately half of the difference between the inner diameter 13R of the outer ring spacer 13 and the inner diameter 22R of the outer ring 22.

軸受装置１の最上部においては、外輪間座１３の両端部３３の内周面と外輪２２の内周面２６とは、ほぼ面一となっている。そして、軸受装置１の上部から下部へ周方向に沿って向かうにしたがって、外輪間座１３の端面３５と外輪２２の端面２７との接触面積が漸次減少し、軸受装置１の最下部においてこの接触面積が最小となっている。なお、軸受装置１の最下部において外輪間座１３の両端部３３の内周面は、外輪２２の内周面２６より、上記内径差分だけ低い位置となっている。   In the uppermost part of the bearing device 1, the inner peripheral surface of both end portions 33 of the outer ring spacer 13 and the inner peripheral surface 26 of the outer ring 22 are substantially flush with each other. The contact area between the end surface 35 of the outer ring spacer 13 and the end surface 27 of the outer ring 22 gradually decreases from the upper part to the lower part of the bearing device 1 along the circumferential direction. The area is minimized. Note that the inner peripheral surfaces of both end portions 33 of the outer ring spacer 13 at the lowermost part of the bearing device 1 are lower than the inner peripheral surface 26 of the outer ring 22 by the above inner diameter difference.

例えば、外輪間座と外輪の内径及び中心軸が一致しており、外輪ハウジングの直径が２０．５ｍｍの従来の軸受装置では、内輪間座と外輪間座との間の径方向の寸法が全周に亘って１．３５ｍｍと非常に狭いものであった。
しかし、前記実施形態に係る軸受装置１によれば、その最下部において当該寸法を最大２．５０ｍｍ程度確保できる。 For example, in the conventional bearing device in which the outer ring spacer and the outer ring have the same inner diameter and central axis, and the outer ring housing has a diameter of 20.5 mm, the radial dimension between the inner ring spacer and the outer ring spacer is all. It was as narrow as 1.35 mm over the circumference.
However, according to the bearing device 1 according to the embodiment, a maximum of about 2.50 mm can be ensured in the lowermost portion.

外輪間座１３の軸方向中央の内周面３４と外輪間座１３の両端面３３とは軸方向中央に向かうにしたがって内径が大きくなるテーパ面３６で連続させてある。
そして、図２に示すように、外輪ハウジング１０の中央の内周面３４の直下において排出孔１５が開口している。排出孔１５は断面円形であり、その開口（取り入れ口）における直径と中央の内周面３４の軸方向寸法とは同じである。上述のテーパ面３６は、当該排出孔１５の周辺においては排出孔１５に向かうにしたがって下方へ傾斜している。 The inner peripheral surface 34 at the center in the axial direction of the outer ring spacer 13 and the both end surfaces 33 of the outer ring spacer 13 are made continuous by a tapered surface 36 whose inner diameter increases toward the center in the axial direction.
As shown in FIG. 2, the discharge hole 15 is opened immediately below the inner peripheral surface 34 at the center of the outer ring housing 10. The discharge hole 15 has a circular cross section, and the diameter of the opening (intake port) and the axial dimension of the central inner peripheral surface 34 are the same. The tapered surface 36 is inclined downward toward the discharge hole 15 around the discharge hole 15.

上述の本実施形態に係る軸受装置１によれば、外輪間座１３の内径１３Ｒが外輪２２の内径２２Ｒに比べて大きく、かつ、外輪間座１３の中心軸１３Ａが外輪２２の中心軸２２Ａに対して下方に偏心している構成である。このため、外輪間座の内径と外輪の内径がほぼ等しく、これらの中心軸が一致している従来の軸受装置に比べて、外輪ハウジング１０と回転軸３との間に形成されている環状空間５０の径方向の最小寸法を、外輪ハウジング１０及び回転軸３の下方部分において広くとることができる。これにより、外輪ハウジング１０に設けられている排出孔１５からエンジンオイルを充分に排出することができ、外輪ハウジング１０と回転軸３との間の環状空間５０にエンジンオイルが滞留することに起因して、エンジンオイルの撹拌抵抗が大きくなるのを抑制できる。この結果、軸受トルクが増大するのを抑制することができる。   According to the bearing device 1 according to the above-described embodiment, the inner diameter 13R of the outer ring spacer 13 is larger than the inner diameter 22R of the outer ring 22, and the central axis 13A of the outer ring spacer 13 is the central axis 22A of the outer ring 22. On the other hand, the configuration is eccentric downward. For this reason, the annular space formed between the outer ring housing 10 and the rotary shaft 3 as compared with the conventional bearing device in which the inner diameter of the outer ring spacer is substantially equal to the inner diameter of the outer ring and the central axes thereof coincide with each other. The minimum radial dimension of 50 can be widened in the lower part of the outer ring housing 10 and the rotary shaft 3. As a result, the engine oil can be sufficiently discharged from the discharge hole 15 provided in the outer ring housing 10, and the engine oil is retained in the annular space 50 between the outer ring housing 10 and the rotary shaft 3. Thus, it is possible to suppress an increase in the stirring resistance of the engine oil. As a result, an increase in bearing torque can be suppressed.

なお、前記実施形態に係る軸受装置１においては、その上側部分において外輪間座１３と外輪２２の端面との当接面積が充分に確保される。このため、外輪２２相互間の軸方向の間隔を保持するという外輪間座１３の機能を損なうことなく、上記効果を奏することができる。
また、前記実施形態に係る軸受装置１は、外輪間座１３自体を偏心形状に形成する必要がないため、外輪間座１３を容易に製造するとこができる。 In the bearing device 1 according to the embodiment, a sufficient contact area between the outer ring spacer 13 and the end surface of the outer ring 22 is ensured in the upper portion thereof. For this reason, the said effect can be show | played, without impairing the function of the outer ring spacer 13 of maintaining the axial space between the outer rings 22.
Further, the bearing device 1 according to the embodiment does not require the outer ring spacer 13 itself to be formed in an eccentric shape, and therefore the outer ring spacer 13 can be easily manufactured.

また、外輪ハウジング１０の内周面１２に、排出孔１５に向かうにしたがって下方へ傾斜するテーパ面３６を設けているため、テーパ面３６に沿ってエンジンオイルが排出孔１５に流れ込みやすくなり、エンジンオイル排出性が向上する。その結果、エンジンオイルの撹拌抵抗が大きくなるのを更に効果的に抑制することができ、軸受トルクが増大するのをより効果的に抑制することができる。   Further, since the inner peripheral surface 12 of the outer ring housing 10 is provided with the tapered surface 36 that is inclined downward toward the discharge hole 15, the engine oil easily flows into the discharge hole 15 along the tapered surface 36. Oil drainage is improved. As a result, an increase in engine oil stirring resistance can be further effectively suppressed, and an increase in bearing torque can be more effectively suppressed.

なお、上述の実施形態では、外輪ハウジング１０と外輪間座１３とが一体形成されていたが、外輪ハウジング１０と外輪間座１３とは別体であってもよい。
また、軸受装置１の最上部において、外輪２５の内周面２６と外輪間座１３の両端部３３の内周面とは、必ずしも面一でなくてもよく、一対の外輪２５の相互の間隔を保持するのに必要な両者の端面の接触面積を確保することができる限りにおいて、外輪間座１３の両端部３３の内周面を、外輪２５の内周面２６よりも径方向外方に配置してもよい。 In the above-described embodiment, the outer ring housing 10 and the outer ring spacer 13 are integrally formed. However, the outer ring housing 10 and the outer ring spacer 13 may be separate.
Further, in the uppermost part of the bearing device 1, the inner peripheral surface 26 of the outer ring 25 and the inner peripheral surfaces of both end portions 33 of the outer ring spacer 13 do not necessarily have to be flush with each other. As long as the contact area of both end surfaces necessary for holding the outer ring spacer 13 can be secured, the inner peripheral surfaces of the both end portions 33 of the outer ring spacer 13 are more radially outward than the inner peripheral surface 26 of the outer ring 25. You may arrange.

１：軸受装置（ターボチャージャ用軸受装置）、２：ケーシング、３：回転軸、５：ケーシングの内周面、６：ケーシング内の側壁面、９：内輪間座、１０：外輪ハウジング、１１：軸受保持部、１２：外輪ハウジングの内周面、１３：外輪間座、１３Ａ：外輪間座の中心軸、１３Ｒ：外輪間座の内径、１５：排出孔、１６：外輪ハウジングの外周面、１７：外輪ハウジングの軸方向の端面、２０：転がり軸受、２２：外輪、２２Ａ：外輪の中心軸、２２Ｒ：外輪の内径、２３：内輪、２４：玉（転動体）、２７：外輪の端面、３５：軸方向の両端面、３６：テーパ面、５０：環状空間   1: bearing device (turbocharger bearing device), 2: casing, 3: rotating shaft, 5: inner peripheral surface of casing, 6: side wall surface in casing, 9: inner ring spacer, 10: outer ring housing, 11: Bearing holding portion, 12: inner peripheral surface of outer ring housing, 13: outer ring spacer, 13A: central axis of outer ring spacer, 13R: inner diameter of outer ring spacer, 15: discharge hole, 16: outer peripheral surface of outer ring housing, 17 : Axial end face of outer ring housing, 20: rolling bearing, 22: outer ring, 22A: central axis of outer ring, 22R: inner diameter of outer ring, 23: inner ring, 24: ball (rolling element), 27: end face of outer ring, 35 : Both end surfaces in the axial direction, 36: tapered surface, 50: annular space

Claims (2)

ケーシング内に設けられ水平な軸方向の中央下部にエンジンオイルの排出孔が形成されている円筒形状の外輪ハウジングと、
前記外輪ハウジングの軸方向両側部それぞれに取り付けられ、外輪、内輪及び転動体を備え前記外輪ハウジングの径方向内側にある回転軸を回転自在に支持する転がり軸受と、
前記内輪の相互間に介在し、前記内輪の相互間の間隔を保持する円筒状の内輪間座と、
前記外輪の相互間に介在し、前記外輪の相互間の間隔を保持する円筒状の外輪間座と、
を有し、
前記ケーシングの内周面と前記外輪ハウジングの外周面との間に供給されたエンジンオイルが、前記外輪ハウジングの軸方向の端面と前記ケーシング内の側壁面との間を経て前記転がり軸受内に供給され、前記転がり軸受を通過したエンジンオイルが、前記内輪間座と外輪間座との間の環状空間から前記排出孔を通じて排出されるターボチャージャ軸受装置であって、
前記外輪間座の内径が前記外輪の内径に比べて大きく、かつ、前記外輪間座の中心軸が前記外輪の中心軸に対して下方に偏心していることを特徴とするターボチャージャ用軸受装置。 A cylindrical outer ring housing which is provided in the casing and has a discharge hole for engine oil formed in a central lower portion in the horizontal axial direction;
A rolling bearing mounted on each of both axial sides of the outer ring housing, and provided with an outer ring, an inner ring, and a rolling element, and rotatably supporting a rotating shaft radially inside the outer ring housing;
A cylindrical inner ring spacer that is interposed between the inner rings and maintains a distance between the inner rings;
A cylindrical outer ring spacer that is interposed between the outer rings and maintains a space between the outer rings;
Have
Engine oil supplied between the inner peripheral surface of the casing and the outer peripheral surface of the outer ring housing is supplied into the rolling bearing via the axial end surface of the outer ring housing and the side wall surface in the casing. The engine oil that has passed through the rolling bearing is discharged from the annular space between the inner ring spacer and the outer ring spacer through the discharge hole.
A turbocharger bearing device, wherein an inner diameter of the outer ring spacer is larger than an inner diameter of the outer ring, and a central axis of the outer ring spacer is eccentric downward with respect to a central axis of the outer ring. 前記外輪ハウジングの内周面に、前記排出孔に向かうにしたがって下方へ傾斜するテーパ面を設けている請求項１記載のターボチャージャ用軸受装置。   The turbocharger bearing device according to claim 1, wherein a tapered surface that is inclined downward toward the discharge hole is provided on an inner peripheral surface of the outer ring housing.
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105422628A (en) * 2015-11-23 2016-03-23 中国舰船研究设计中心 Novel water-lubricated rubber stern bearing
WO2017042925A1 (en) * 2015-09-10 2017-03-16 三菱重工業株式会社 Bearing device for turbocharger, and turbocharger

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6147434U (en) * 1984-09-03 1986-03-29 石川島播磨重工業株式会社 Turbocharger bearing device
JPS6235195U (en) * 1985-08-22 1987-03-02
JPH0231354U (en) * 1988-08-23 1990-02-27
JP2010133266A (en) * 2008-12-02 2010-06-17 Toyota Motor Corp Bearing device for supercharger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6147434U (en) * 1984-09-03 1986-03-29 石川島播磨重工業株式会社 Turbocharger bearing device
JPS6235195U (en) * 1985-08-22 1987-03-02
JPH0231354U (en) * 1988-08-23 1990-02-27
JP2010133266A (en) * 2008-12-02 2010-06-17 Toyota Motor Corp Bearing device for supercharger

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2017042925A1 (en) * 2015-09-10 2017-03-16 三菱重工業株式会社 Bearing device for turbocharger, and turbocharger
US10161265B2 (en) 2015-09-10 2018-12-25 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Bearing device for turbocharger, and turbocharger
CN105422628A (en) * 2015-11-23 2016-03-23 中国舰船研究设计中心 Novel water-lubricated rubber stern bearing

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